Electrical Machine and Its Bearings

ABSTRACT

The invention aims at increasing the critical speeds of rotation of an electrical machine while using standard components. Therefor, a shaft ( 11 ) is housed in the electrical machine by means of a fixed bearing ( 5, 6 ) and a free bearing ( 4 ). The fixed bearing is formed by two grooved ball bearings which are respectively prestressed in opposite directions by springs. Thus, at least one of the two grooved ball bearings is always prestressed independently of the axial force exerted on the shaft ( 11 ), such that the required radial stiffness of the fixed bearing is guaranteed.

The present invention relates to an electrical machine having a housing,a first bearing device, which is in the form of a movable bearing, asecond bearing device, which is in the form of a fixed bearing, and ashaft, which is mounted with the two bearing devices in the housing suchthat it can rotate.

The radial resilience of rolling bearings has a substantial influence onthe operational response of machines since, owing to the additionalelasticity of the bearings, the bending-critical speeds of the rotorsare reduced in comparison with the ideal rigid mounting. Rollingbearings also generally have a lower rigidity in the horizontaltransverse direction than in the vertical transverse direction since theradial prestress there is not provided by the rotor weight. This resultsin the natural bending forms being split into a horizontal and avertical natural bending form, in which case the horizontal one is lowerin terms of frequency and therefore oscillation and noise problems areto be expected even at lower speeds.

In practice, this problem is solved in a known manner by rollingbearings being used which can be axially prestressed, for example deepgroove ball bearings or angular ball bearings. Above all, the horizontaltransverse rigidity of the bearings and therefore also the possiblespeed range of the machine are therefore increased. In addition, thenoise response and the service life of the bearings are positivelyinfluenced.

DE 196 54 089 A1 has disclosed a deep groove ball bearing, in the caseof which axial prestress is achieved within the bearing by the rollingbodies being pushed alternately axially into one and the opposite endposition of the running surfaces by construction elements of the cage.Accordingly, the bearing used is not a bearing which is available asstandard. DE 689 04 444 T2 and DE 36 26 626 C2 also describe specialconstructions of rolling bearings having the option of axial prestress.These variants likewise have the disadvantage that the solutions excludestandard components.

DE 42 24 980 A1 describes a design solution which uses standard rollingbearings and prestresses the bearings in one direction so severely thatexternal loads can bring about a fluctuation in the value of the axialprestress but cannot bring about a reversal of direction. This approachsolves the problem in principle, but high static loads on the bearingsare even produced within the machine which reduce the service life.

DE 30 38 112 A1 describes a construction with an axial prestress of thebearings which can be adjusted and readjusted. In this case too, somespecial elements are required and the inner ring of a bearing needs tobe designed to be displaceable on the shaft. Since the inner ring inmany cases has circumferential load, there is the risk with this variantof frictional corrosion.

In the case of a floating mounting, which is generally known, the twobearings are prestressed, but the rotor is not mounted in a staticallydetermined manner, i.e. it has a degree of translatory freedom in theaxial direction.

The object of the present invention consists in proposing a mountingsystem in the case of an electrical machine in which thebending-critical speeds are as high as possible and standard componentscan be used.

This object is achieved according to the invention by an electricalmachine having a housing, a first bearing device, which is in the formof a movable bearing, a second bearing device, which is in the form of afixed bearing, and a shaft, which is mounted with the two bearingdevices in the housing such that it can rotate, the second bearingdevice having two deep groove ball bearings, which are prestressed withrespect to one another in each case by a spring device.

In an advantageous manner, rolling-bearing mounting of the rotor of anelectrical machine can therefore be provided which axially guides therotor using simple deep groove ball bearings and spring elements andwhich applies a minimum axial prestress to all the bearings of theelectrical machine, which prestress cannot be canceled by external axialforces on the rotor.

Rotor windings can be arranged on the shaft between the two bearingdevices. With the fixed bearing construction according to the invention,it is therefore possible to permanently maintain the high radialrigidity of the deep groove ball bearings and, as a result, to achieve ahigher maximum speed.

The two inner rings of the deep groove ball bearings are preferablyspaced axially apart from one another by a spacer. As a result, theouter rings of the two deep groove ball bearings can be displaced in theaxial direction independently of one another by the spring devices, withthe result that axial prestress is always ensured.

A securing element can secure the deep groove ball bearings axially onthe shaft. In addition to the frictional force which results, forexample, from the bearing inner rings being shrunk onto the shaft, it istherefore ensured that axial forces can be transmitted via the bearingto the housing.

In one preferred embodiment, the spring devices each act on the outerrings of the deep groove ball bearings. In principle, the spring devicescould also act on the inner rings, in which case it would be necessaryfor the outer rings to be fitted tightly in the housing. However, thiswould have disadvantages in terms of fitting.

It is further preferred if the spring devices each have a helicalspring, with which they apply the prestress force. Such helical springsare simple in terms of production and cost-effective. In principle,hydraulic, pneumatic, electrical, magnetic and other spring elementscould also be used, however.

At least one of the outer rings of the deep groove ball bearings canalso be inserted into the housing with a transition fit. This means thatthe outer ring can be displaced axially but the mounting in the radialdirection is nevertheless determined.

Furthermore, one of the outer rings of the deep groove ball bearings canbe rotated freely and radially in the housing. This has the advantage ofa clear division of load between the two deep groove ball bearings.

The present invention will be explained in more detail with reference tothe attached drawings, in which:

FIG. 1 shows an electrical machine mounted in a conventional manner;

FIG. 2 shows an electrical machine mounted according to the invention ina basic diagram; and

FIG. 3 shows a specific exemplary embodiment of an electrical machinemounted according to the invention.

The exemplary embodiment described in more detail below represents apreferred embodiment of the present invention.

The invention comprises a known and extended rolling bearing mountingsystem (FIG. 1). This mounting system is incorporated in any desiredhousing construction 1, 2, 3. A deep groove ball bearing 5 with a tightfit on the inner and outer ring is used as the fixed bearing. Themovable bearing is formed by a deep groove ball bearing 4, which has aloose fit on the outer ring. The outer ring can be displaced by acompression spring 7. The two inner rings of the bearings are securedaxially on the shaft 11 by securing elements 13, 14. The axial adjustingforce of the spring 7 is transferred to the fixed bearing 5 via therotor 11, 12. However, it can be compensated for by an external axialforce (for example tensile force on the shaft 11), with the result thatthe fixed bearing 5 runs free of axial force.

The invention uses the same movable bearing principle according to thebasic illustration in FIG. 2. Two deep groove ball bearings 5, 6 areused instead of one as the fixed bearing, the inner rings of said deepgroove ball bearings resting tightly on the shaft 11 and the deep grooveball bearings being spaced axially apart by a spacer element 15. Asecuring element 14 secures the inner rings on the shaft axially. Theouter rings of the two bearings are inserted with a loose fit into thesurrounding housing part 3. Owing to the loose fit, which is alsoreferred to as a transition fit, it is possible to achieve a situationin which the outer rings can be axially displaced with respect to thehousing part 3. At the same time, the transition fit ensures sufficientradial rigidity. One of the two outer rings can also be incorporatedsuch that it is rotated freely and radially, however, as a result ofwhich the corresponding bearing can only accommodate axial loads forreasons of clear load division.

The two bearings 5, 6 of the fixed bearing are fixed axially by thesurrounding housing 3, and the outer rings are adjusted by springelements 8, 9 such that the spring forces point in the direction of thegap produced by the spacer element 15. The direction of the adjustingforce of the spring 7 of the movable bearing 4 can be selected asdesired.

In the present refinement of the mounting system, the axial adjustingforce of the movable bearing 4 has the value of the force of the spring7 reduced by the frictional force of the outer ring in the housing hole2, irrespective of an external axial force. The axial force which intotal needs to be absorbed by the fixed bearing 5, 6 is calculated fromthe vectorial addition of the external force acting on the shaft 11, theforce of the spring 7 of the movable bearing 4 and the frictional force.Depending on the absolute value for and direction of this total force,only the force of the respective spring 8 or 9 reduced by the associatedfrictional force is applied axially to a bearing 5 or 6 in the case ofthe fixed bearing, and the other bearing has the total force applied toit. This total force acts in the bearing and is absorbed on the outerring proportionally by contact force in the housing. In any case, theaxial prestress of one of the two bearings has at least the value of theassociated spring adjusting force reduced by the frictional force. Sinceone of the two bearings 5 or 6 is now always prestressed irrespective ofthe axial force on the shaft 11, the required radial rigidity of thefixed bearing is always maintained. As a result, it is possible to avoida situation in which the corresponding radial rigidities are reduced andthe machine tends towards higher oscillations and noise values as aresult of a state of the overall bearing or one of the two deep groovebearings 5 or 6 which is free of axial forces.

FIG. 3 reproduces a specific embodiment of an electrical machineaccording to the invention which is based on the basic illustration inFIG. 2. The spring elements 7, 8 and 9 are in this case specifically inthe form of helical springs. This embodiment of a spring element isrelatively cost-effective and robust in comparison with otherembodiments.

According to the invention, simple standard components are used, withoutdispensing with the axial guidance of the rotor by means of the optionfor axial movement of all the outer rings of the mounting system in atleast one direction and the action of spring forces on all outer rings,to achieve a situation in which, under any desired external axial force,no bearing can run free of axial forces.

The advantages of the bearing design according to the invention are asfollows:

-   1. Increased radial rigidity by means of prestressing the bearings    and therefore higher maximum operating speed;-   2. Reduction in bearing noise;-   3. No risk of premature damage to bearings owing to on-load    operation;-   4. No special components required.

1.-8. (canceled)
 9. An electrical machine, comprising: a housing; afirst bearing device constructed as a movable bearing; a second bearingdevice constructed as fixed bearing having two deep groove ballbearings; a spring device for prestressing the two deep groove ballbearings to one another; and a shaft rotatably supported by the firstand second bearing devices.
 10. The electrical machine of claim 9,further comprising rotor windings arranged on the shaft between thefirst and second bearing devices.
 11. The electrical machine of claim 9,further comprising a spacer, said two deep groove ball bearings beingspaced axially apart from one another by the spacer.
 12. The electricalmachine of claim 9, further comprising a securing element for securingthe deep groove ball bearings axially on the shaft.
 13. The electricalmachine of claim 9, wherein the spring device includes a first springelement acting on an outer ring of one of the deep groove ball bearings,and a second spring element acting on an outer ring of the other one ofthe deep groove ball bearings.
 14. The electrical machine of claim 9,wherein the spring device includes a helical spring.
 15. The electricalmachine of claim 13, wherein at least one of the outer rings of the deepgroove ball bearings is inserted into the housing with a transition fit.16. The electrical machine of claim 13, wherein one of the outer ringsof the deep groove ball bearings is rotated freely and radially in thehousing.